Justifying mechanism.



No.'848,809. PATEN'I'ED APR. 2,.1'907.

" F. B. CONVERSE, JR.

JUSTIPYING MECHANISM.

APPLICATION TILED SEPT. 4, 1903.

. rue NORRIS PETERS cm, WASHINGTON, n. c

No. 848,809. PATENTED APR. 2, 1907. F. B. CONVERSE, IR. JUSTIFYINGMECHANISM.

APPLICATION FILED SEPT. 4, 1903.

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110,848,809. PATENTEDAPR.2,1907.

P, B. 'OONVERSEJR. JUSTIFYING MECHANISM.

APPLICATION FILED SEPT. 4", 1 903.

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Nox 848,809. PATENTED APR. 2} 1907. F. B. CONVERSE, JE- I I JUSTIPYINGMECHANISM.

11 SHEETS-SHEET 5.

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No. 848,809. PATE NTED APR. 2', 1907. F. B. CONVERSE, JR.

'JUSTIPYING MECHANISM. APPLICATION FILED SEPT. 4, 1903.

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1n: NORRIS PETERS ca. WASHINGTON, n. c

PATENTED APR. 2, 1907.

P. B. CONVERSE, JE- JUSTIFYING MECHANISM. APPLICATION FILED SEPT. 4,1903.-

11 SHEETS-SHEET 7.

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PATENTED APR. 2, 1907. P. B. CONVERSE, JR, JUSTIFYING MECHANISM.

. APPLIOATION'IILED SEPT.4,1903.

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No. 848,809. PATENTED APR. 2, 1907.

P; B. CONVERSE,- In. JUSTIFYING MECHANISM.

APPLICATION FILED SEPT. 4, 1903. 4

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.No. 848,809. PATENTED APR. 2, 1907.

-' P. B. CONVERSE, JR;

JUSTIFYING MECHANISM. APPLIOATiOiI FILED sum 1903.

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No. 848,809. PATEN-TEDAPR. 2, 1907. F.B.QONVERSE,JE.

JUSTIFYING MECHANISM.

APPLICATION FILED SEPTA, 1903.

11 SHEETS-SHEET 11.

. i ll 2 II 3 l i I fi i'tneu'ofeis. 122,5071

rns mum's PETERS co., wumrvaruu, n. c.

UNITED STATES PATENT OFFICE.

FRANCIS B. CONVERSE, JR, OF CLEVELAND, OHIO, ASSIGNOR, BY MESNEASSIGNMENTS, TO THE CLEVELAND TYPESETTER COMPANY, OF CLEVE- LAND, OHIO,A CORPORATION OF OHIO.

JUSTIFYING MECHANISM.

Specification of Letters Patent.

Patented April 2, 1907.

Application filed September 4, 1903. Serial No. 172.001.

To all whom it may concern.-

Be it known that I, FRANCIS B. CONVERSE, Jr., a citizen of the UnitedStates, residing at Cleveland, in the county of Cuyahoga and State ofOhio, have invented a certain new and useful Improvement in JustifyingMechanism, of which the following is a full, clear, and exactdescription, reference being had to the accompanying drawings.

General statement.The object of this invention is to provide a simple,efficient, and rapidly-operating machine for the automatic justificationof type. The term type is used herein as including both the cameo formor ordinary printers type and the intaglio form or matrices in which theprintingface may be cast.

The machine is adapted to operate in conjunction with any form oftypesetting-machine which is capable of delivering to it an assembledline of type with interposed temporary spaces at points in the linewhere regular type-spaces are to be inserted and in conjunction with anysuitable mechanism for taking care of the justified line, as by delivering it into a galley.

A complete machine embodying the present invention includes thefollowing cooperating mechanisms: first, a suitable channel for carryingthe line of type as it comes to the machine; second, a space-recordingmechanism which takes account of the number of spaces in the line;third, a line-measuring mechanism which measures the amount by which theline set up is different in length from the desired line as justified;fourth, a space-selecting mechanism which operates according to thenumber of spaces in the line and the'variation in length of the line,being controlled by the two preceding mechanisms to determine the propersize of space required; fifth, a mechanism called the fractional spacingmechanism, (which is really a portion of the space-selecting mechanism,)effective when the line will not exactly justify with but one size ofpermanent space, whereby a portion of one size and a portion of anothersize may be used to make the proper aggregate thickness;-sixth, aline-advancing mechanism to carry the line through the justifyingmechanisms; seventh, a spacesubstitutingmechanism which acts as suchline is advanced to, replace the temporary spaces by permanent spacesselected of the proper thickness.

The present invention is concerned with the space selecting andfractional spacing mechanisms, the other mechanisms being shown toclearly illustrate the complete operation. -Many features of these othermechanisms are covered in my prior patents, Nos. 717,169 and 738,741,issued December 31, 1902, and September 8, 1903, respectively, and myprior pending applications, Serial No. 3,280, filed January 30, 1900,and Serial No. 4,124, filed February 5, 1900.

Drawing's.1n the drawings the justifying system is shown as embodied ina machine for operating on ordinary printers type, and such embodimentwill now be described.

Figure 1 is a front elevation of the ma chine, the upper portion of thespace-case being broken away and the delivery mechanism being omitted.Fig. 2 is an end view taken from the left-hand end of Fig. 1. Fig. 3 isan end view taken from the right-hand end of Fig. 1, sectioned throughone of the operating shafts known as the wordshaft. Fig. 4 is a verticalsection of the machine through the fractional spacing mechanism, beingon the line 4 4 of Fig. 1. Fig. 5 is a vertical section parallel withFig. 1, being taken on the line 5 5 of Fig. 2 looking to the rear. Fig.6 is a vertical section parallel with Fig. 1, taken on the line 6 6 ofFig. 2 and looking to the front. of the machine. Fig. 8 is a horizontalsection on the line 8 8 of Fig. 2. Fig. 9is a rear elevation sectionedthrough the hubs of the clutch members on the two shafts, as indicatedby the line 9 9 of Fig. 2. Fig. 10 is a face view of the fractionalspacing mechanism looking at the rear side of the same, being anenlargement of a portion of Fig. 6. Fig. 11 is a view of the temporaryspace employed. Figs. 12 to 17 are details of the fractional-spacingmechanism, Fig. 12 being a side elevation of the box of plungers, Fig.13 a bottom view thereof, Fig. 14 a top view thereof. Figs. 15, 16, and17 are crosssections of the box of plungers for a two-space line, aten-space line, and a twelve-space line, respectively. Fig. 18 is adetail showing the spacerecording pawls in place. Fig. 19 is a $5 Fig. 7is a plan plan of the justifying-channel, showing the word-shaft tri pand gap-opener, omitting the space-turner; and F1g. 20 1s a verticalsection through the ustifyingchannel, showing such word-shaft trip; Q,SPlCG-BJBCtOT, .l't, temporary space; Z, type.

1* TCLWL6.-T he various mechanisms for the most part are carried by avertical plate A,

which is supported on a suitable bed and extends lengthwise through themachine. On the upper end of this plate is mounted a horizontal plate A,having in it a longitudinal recess a, which constitutes thejustifying-ch annel. The line oftype Z,with interspersed temporaryspaces R, is fed into this channel through an opening a thereinto fromthe rear, Figs. 7 and 9, and the completely-justified line is fed out ofthe channel at the righthand end of Fig. 1. Secured to the front side ofthe plate A is a bracket in the form of a narrow vertical plate A whichassists in carrying the space-selecting and fractional.- spacingmechanisms. The main operatingshafts D and N extend through the plate Aand are journaled therein and also in four standards, two on each sideof the plate, (designated A A, A and A?) Space-recording mechanism.-Thespacerecording mechanism is adapted to be a tuatcd once for eachtemporary space in the line. This may be accomplished by the temporaryspaces themselves after the line is assembled or by the operation of thespace-key in the setter, which acts as the line is being assembled. Themechanism therefor is best shown in Figs. 5, S, 9, and 18.

In F ig. 9, 0 indicates an operating-link for the space-recordingmechanism, which may be connected directly at its upper end with thespace-key lever of the setter. In any case it is adapted to be drawnupward once for each space in the line. This link is connected at itslower end with a rock-arm c on a rock-shaft c, which carries another arma", carrying a pawl 0 This pawl is adapted. to engage teeth on a block 0slidable upon a gib c and feed the block to the left in Fig. 9 a toothat a time as the link C is elevated. A pawl 0 Fig. 18, similar in shapeto the pawl and directly behindv it, retains the block 0 againstretrograde movement, a spring c giving the block a tendency in suchreturn direction. Thus the block 0 takes a position dependent upon thenumber of spar-es in ihe line.

On the front side of thcplatert is a sta1ionary rack c, Figs. 5 and 8,having teeth corresponding to the teeth on the block 0''. Slid able ongibs c on the front side of the plate A is a plate 0, which carries aplunger-pawl 0, adapted to engage with the teeth of the rack c andconnec ed by a lever c" wit h another plunger pawl 0' Fivoted to blockan arm 0 pressed toward the plate A by a spring 0 and. having aninclined shoulder c. Now after the block 0" has been positionedaccording to the number of spaces the plate (1" at the pro ier timemoved in the extreme right by reason of the ram r. Fig. 5, shoving onthe roller 0 on a linlc coni'iected. to the plate. The right-lnmd endtooth of the rack projects forward sl'ighlly fartl'ier than the otherteeth of this rack. the pawl c is advanced against this too'i h in themrwement of the plate iirst referred to the pawl is forced forward farenough in per mit it to clear the-other teeth of the rack c as the platemoves to the left. Following tin extreme movement of the plate to theright a weight on the cord 0, com'iected to the link 0", moves the plateto the left until the i'ial end of the plunger-pawl engages the inclinec on the arm 0. Thcreupon this )lnnger-pawl will be forced forward andthe plun gerqaawl 0 will be thereby forced rcarwaad locking the plate 0to the stationary rack r in a position which is a number of teel h fromthe left of the rack 0* corresponding to she tooth. of the block 0engaged by the pawl w. Thereafter the cam-piece a (on the fern ard sideof the cam f, Fig. 9) presses down the adjacent end of the pivotedvlever 0 w ose other end carries a pin (9, Fig. b4, hen ath the tails ofthe two pawls c" and c", and his action moves these pawls to release theblock to allowit to be returned to its origiinal position by the spring0. Thus the I'mord of the number of spaces is transferred from the block0' to the plate a and the forn'ier is at once ready for taking accountof the number of spaces in the succeeding line as it is being assembled.

The machine shown for convenience is a r ranged. to operate on lineshaving anywhere from two to twelve space: between words. Thetheoreticallypossible one-spa -c line is not provided for in themechanism, as it practically never occurs in actual operation. Thereforethe position of the parts shown in Fig. 8, wliere the pawl c engages theli'lth tooth. of the rack c, is for a line having six temporary spaces.

Linc-measuring mechanicm.-Tl1e assen1- bled line, with thetemporaryspaces in 'lilzlfl, is fed by suitable mechanism (not showniinto a position in the justifying-channel ll-T just in front of the pawl6, Figs. 6 and 7, which forms an abutment against which the line is tobe measured. The measuring mechanism proper comprises a wedge and meansfor feeding it upward against the right-hand end of the line to compactthe line against the abutment and the mechanism for'operating the wedge.These features are best shown in Figs. 5 and 6.

F indicates the wedge, which along its in clined edge has atongue-and-groove connection f with a stationary gibf. The righthandedge of the wedge in Fig. 6 is vertical and stands at a distance fromthe end of the pawl b, theoretically just equal to the required lengthof lineor column width, practically a slightly greater distance. Thusthe distance between the vertical edge of the wedge and the end of thetype (shown in Figs 6 and 7 as Z) is equal to the amount which theunjustified line is less than the column width (or the line shortage)plus a small amount of allowance to permit the wedge to rise a shortdistance before reaching its true zero position. This allowance isrepresented by the distance between the pin it and bar f hereafterreferred to. Now as the wedge moves upward it travels toward the type(owing to the sliding connection by its inclined edge) until it isstopped by taking up this shortage, compacting the line against the pawlb, wherefore the travel of i the yvedge is dependent upon the shortageof the The wedge carries at its lower end a horizontal grooved extensionf in which takes a pin f 3 on the upper end of a barf which is given anupward tendency by a weight (not shown) pulling down on a cordf whichpasses over a pulley f G and is secured at its lower end to the barf. Onthis barf are teeth which mesh with the teeth of a gearf which is on ashort shaftf journaled in the plate A. On the rear end of the shaft f isa pinionf, Fig. 9, meshing with teeth on a link f the iree end of whichis guided by the gibf the other end yoking around one of the main shaftsD (known as the line-shaft) and carrying a rollerf adapted to bearagainst the periphery of a cam f on that shaft. It thus results thatwhen upon rotation of the shaft D a decreasing face of the cam f allowsit the weight, pulling downward on the cord will raise the wedge untilit is stopped. by compacting the line, the wedge remaining in thisposition until the increasing face of the cam draws it down to normalposition.

The sh aft D is given one complete rotation for each line. This rotationis initiated by the link (1, Figs. 2 and 9, which is drawn upward by theoperator at the end of the line, and this movement withdraws the end ofthe lever d (to which the lower end of the link is connected) fromengagement with a pawl (Z carried by a disk d rigid with the shaft D,whereupon this pawl is forced by a spring (Z into engagement with acontinuously-rotating notched member d. This causes the lineshaft D torotate until as one rotation is completed the tail of the pawl (Zengages the end of the replaced lever (1, and thus the pawl draws itselfout of engagement with the notched member (Z bringing the line shaft torest. For convenience of illustration this lineshaft is shown herein ashaving made something less than the half-rotation from its position ofrest. Now one of the first operations of the line shaft D is to causethe cam c to position the space-recording plate c as already explained,and this positioning of the plate brings into a corresponding definiteposition a vertical rack H. This rack is secured to the left-hand edgeof the plate by the gib 0 which permits a free vertical movement of therack upon the plate 0. After this positioning of the rack H mechanism,shortly to be described, comes into operation and moves a series ofgears G (hereinafter more fully described) rearward until stopped by theside of some gear overhanging and en gaging the side of the rack, therack meshing with the next smallest gear. This is the po sition of theparts shown in Fig. 8. In this position the wedge begins to rise, andthe eX- tensionf thereof engages a pin h, Figs. 5 and 6, extendingrearward from the rack H, and this raises this rack a distanceproportionate to the line shortage. his gives to the periphery of thegear G, which is in engagement, a like movement. Suitable mechanism (tobe hereinafter described) acts as a friction-brake on the series ofgears and prevents their return rotation, and hence they hold the rack Helevated, and the wedge returns idly.

sponse-selecting mechanism.The system of gears G referred to consists ofseveral gears, of radii increasing in an arithmetic ratio, arranged in acone. The number of these gears is theoretically equal to the maximumnumber of spaces in any line which may be justified by the machine,though for convenience of construction the gear for a one-space line isomitted, being unnecessary. Thus, as shown in the drawings, there areeleven gears, and this provides for lines having from two to twelvespaces to be justified,

larger number of gears than those shown may-be employed. The radius ofthe smallest of the complete series of gears being one unit-that is, theomitted gear which would be brought into use in the justification of aline containing one spacethe radius of the next gear is two units, (fora two-space lin.e,) the radius of a three-space gear is three units, andso on, the radius of each gear being many times that of the gear for onespace as there are spaces in the line with which the given gear isdesigned to operate. 7

The gears G are all rigid with a shaft g, which is slidably androtatably mounted in the frame-plate A and. the frame-bracket A Figs. 4and 8. On the forward end of this shaft is a collar g, into which takesa pin 9 carried by the upper end. of a lever 9, Figs. 1. and 2, which ispivoted to a small framestandard A and is given a constant tendency tomove rearward by a suitable downward pull on a bell-crank arm g of saidlever. This pull may be a weight (not shown) on the end of a link 9 Thislever carries a roller 9, which is adapted to be actuated by thecrown-cam g on the line-shaft D. Now the cam g is so placed thatimmediately preceding the locating of the plate 0 the increasing face ofthis cam acts on the roller 9 to move the series of gears to the front,taking them all out of the path of the rack H. The cam 0 then acts tolocate the plate 0 and the rack H, as heretofore fully described. Following this and before the wedge rises the decreasing face of the cam gallows the lever to move rearward until one of the gears G meshes withthe rack H, as heretofore stated. The gears G are normally held at azero position by reason of a spring 9 Fig. 9, secured to a strap g,which is fastened to the periphery of a small drum on the shaft g. Inthe zero position of the gears G every gear has a tooth on the sidetoward the rack H in the same horizontal plane, which plane passesthrough the center of the shaft g, whence it follows that the rack H maymesh with any gear which the space-recording mechanism determines. Nowthe position of the plate 0, if there were but one temporary space inthe line, would be such that the rack H would mesh with the smallest ofthe complete theoretic series of gears G. If there were two temporaryspaces in the line, the plate 0 would be positioned one tooth. to theright, Figs. 5 and 8, which distance would just allow the next gear ofthe series (the first one shown) to mesh with the rack, and so on. Thisis the position shown in Figs. 2, t, and 5. Thus that gear meshes withthe rack which corresponds to the number of spaces in the line. The gearfor the one-space line being omitted, it takes two depressions of thespace-key, acting through. the block 0 and the plate 0, to bring therack H into the position. shown in Fig. 5, where it engages the smallestactual gear. It takes six depressions to bring it into the position.shown in Flg. 8.

eaaeoe It will be seen that the rotation which the rise of the wedgegives to the shaft 9 is dependent upon the two factors of the number ofspaces in the line and the line shortage. The greaterthe shortage thegreater the rotation for a given number of spaces, or, eonverselystated, the greater the number of spaces the less the rotation. for agiven short age. This relation may be stated as a ma thematical formula.Let R equal amount of rotation. of shaft 9, N equal number of Sj')2-.t(.S equal line shortage, 0 equal a constant dependent on theactualproportion of the part s.

Then R equals The rotation of the shaft 9 is thus proportional to thequotient obtained by dividing the line shortage by the number of spaces,and this quotient is, moreover, the theoretic size of space required toexactly justify the line.

The permanent spaces which are selected by this machine and inserted inthe line in place of temporary spaces are contained in channels in avertical space-case 1, Figs. '1 l. 6, and 7. This space-ease is dividedinto several channels, (nine being shown) and (:lt'll of these channelscarries a different size of permanent spaces, (each size differing fromthe adjacent sizes by a uniform amounhi the spaces lying on their flatside and being arranged in the order of their thicknesses, the thinnestspace in the left-hand channel, Fig. 1, and the thickest space in theright-hand channel. The space-case extends upward such a distance thatit may be pivoted above and at its lower end swing a short distant-e insubstantially astraight line to bring any one of the channels in linewith the spaeeejector The spacecase is positioned by means of a barwhich engages its lower end and carries a block 7', adapted to engagewith any o f t h e steps of the plate J, according to the position ofthe plate. Yoking around a pin projerting from the bar is an armjournaled on the stud j and having a bell-crank arm j" with whichconnects a link j, carrying a roller 7', adapted to be engaged b a earni A spring j acting on the arm tends to counteract the cam.

The first movement of the line-shaft l) is to cause the cam 4' to act011 the roller j, and thus shift the space-case to the extreme le ti asshown in Fig. 1. In this position. it is held while the largerconcentric face of the cam j is rotating past the roller. During thistime the rotation of the gears G, heretofore 1nentioned, has positionedthe plate J by nieehanism about to be described, and then when thedecreasing face of the cam j allows it the spring moves the space- :aseback toward the right until stopped by the block j engaging one of thesteps of the plate J. The position of the space-case, and hence the sizeof spaces to be injected into the line, is therefore dependent upon theposition of the plate J, each of the steps of that plate correspond ingto one size of permanent spaces.

The plate J is vertically slidable by means of a vertical bar j Figs. 4,6, and 10, connected therewith and dovetailed between gibs 3' 7' Thelower end of the bar j is extended horizontally, and in this extensionis formed a groove in which takes a rib along the upper edge of theplate j. This plate 7' thus makes a downward extension of the plate J,though it may move crosswise with. reference thereto. A spring jconnects the plate 7' with the bar j and tends to move that plate towardthe left in Figs. 6 an d 10, thus causing its left-hand end to alinewith the left-hand end of the extension j.

Surrounding the shaft g, upon which is keyed the cone of gears G, is asleeve g, rigidly clamped between the largest gear and the collar g.Slidably splined to this sleeve is a gear 9 This gear has its bearing inthe bracket A, being held in place by a nut 9 The hub of the gear formsa slidable bearing for the cone-of-gears shaft. This gear 9 meshes withgear-teeth in the under edge of a bar j, slidably mounted on the T-railj and having its upper edge stepped into as many steps as there aredifferent sizes of permanent spacesnine in this case.

Between the steps of the bar j and the lower edge of the plate j are aseries of plungers K, contained in a suitable frame is, slidably securedby gibs 76 rigidly carried by the bracket A This series of plungersconstitutes a portion of the fractional-spacing mechanism and will behereinafter described. For the present it is suflicient to say that theyconstitute distance-pieces between the steps of the bar j and the plate3' In the zero position of the gears G the bar j is at its extreme left,as shown in Fig. 6. The plungers K may thus engage the lowest step ofthat bar which will bring down the plate J to its lowermost position,allowing the stop y to rest on the extreme left-hand step of that plate,positioning the space-case in its extreme left-hand position, Fig. 6,(that is, its extreme right-hand position, Fig. 1,) with the thinnestsize of spaces in the line with the ejector Q. Now the thinnest size ofthe permanent spaces is the same size as the temporary spaces employed.If the line as first set up should be just the required length, thewedge would rise only the distance between the bar f 2 on the wedge andthe pin 7t on the rack H, and the gears G would not be rotated, the barj would remain in its zero position, and the plate would position thespace-case for the smallest size of spaces. If, however, there is anyline-shortage, (which of course there almost always is,) it is becausespaces larger than the temporary spaces are required to fill the line.This short age, allow ing the wedge to rise above the position justdescribed, rotates the gears G and shifts the bar j according to thesize of space required, as is now to be explained. The rise of each stepon the bar j is equal to the rise of a step on the plate J, and thelength of each step on this bar 7' is the amount which the bar will beshifted when the shaft 9 is rotated through the angle corresponding toan increase of one unit in the size of spaces 'required in the line.There are as many steps on the bar j as there are different sizes ofpermanent spaces, and each step corresponds to a size. The actual lengthof the steps on the bar j is dependent upon the proportions of theparts. For example, the gear g, which engages the bar 3' is shown of thesame size as the largest one of the gears G that is, the gearcorresponding to the twelve space line. If there were twelve spaces inthe line and this largest gear were in action and if the diflerencebetween successive units of permanent spaces is one-hundredth of an inchand if the taper of the wedge is one to six, then the total differencebetween all the spaces of one size and all of the next would be .12 ofan inch and the rise of the wedge would be six times this amount, or .72of an inch. This would give a corresponding movement to 'the peripheryof the gear g, and hence to the bar j wherefore in that instance thelengths of the steps on the bar would be .72 inch. Now the bar f movingone step when the gears are rotated the angular distance correspondingto the distance between successive units of spaces it follows that ifthe parts are so placed that the plungers K engage the extreme end ofthe lowest step for the smallest size of spaces they will occupy thesame position on the second step when the second size of space isrequired and the next step for the third size, and so on. Usually thebar 7' will assume a position such that the plungers will rest upon astep, but will overhang the step next lower, as shown in Fig. 10,because the theoretic size of space required is intermediate of any ofthe existing sizes. This initially places the permanentspace case in thesame position as if all the plungers were engaging the higher step; butthe fractional-spacing mechanism about to be explained will during thesubstitution cause the overhanging plungers to move down onto the nextstep, shifting the spacecase and causing the insertion of a differentsize of spaces. This initial location of the spacecase takes place whilethe concentric face of smallest radius of the cam f is passing the rollf 13 of the link f which controls the movements of the measuring-wedgethat is, while the wedge is in its highest position in the act ofmeasuring the line. The plungers K, pressed downward by the tension ofthe spring j against the stepped bar 7' form a friction-brake whichprevents the spring 9 secured to the drum 9 on the rear ITO end of theshaft 9, from rotating the gears in a reverse direction when the wedgedescends.

Fractional-spacing mcclzantsm.-As suggested, it will happen that mostlines will require more than a single size of spaces to properly justifythem, it not being practicable to carry in the machine enough differentsizes of spaces to permit all lines to be sufficiently closely justifiedby the insertion of only a single size. It is therefore necessary toprovide means for the selection of a portion of the spaces in any lineof one size and the remainder of the spaces of another size, preferablyof the next adjacent sizein the machine as at present constructed. ofthe next smaller size. Thus, by way of illustration, the spaces used inthe present machine are three-hundredths, four-hundredths,fivehundredths, six-hundredths, etc, of an inch in thickness, each sizebeing one-hui'idredtl'i of an inch thicker than the preceding size. Nowif the line to be justified contains seven spaces and is, exclusive ofthe temporary spaces in the line, thirty-eight hundredths of an inchshort, seven spaces each five-hundredths of an inch in thickness, ifinserted, Would aggregate thirty-five hundredths and leave the linethree-hundredths of an inch too short and seven spaces eachsix-hundredths of an inch and make the line fourhundredths of an inchtoo long; but the proper justification of this line can be accomplishedby inserting three six-hundredthsofan inch spaces (amounting toeighteenhundredths) and four five hundredths ofaninch spaces, (amountingto twenty-hundred.ths,) the aggregate of which is equal to the requiredthirty-eight hundredths of an inch. It is necessary, therefore, that thespace-case be moved after the insertion of the first three spaces tocause the remaining spaces inserted in this line to be of the next sizesmaller. Mechanism for doing this (called the fractional-spacingmechanism) will now be described. This mechanism operates duringjustification of the line as temporary spaces are being replaced bypermanent spaces to shift the space-case at the proper time whenever theinsertion of the next smaller size of space should begin. Thisfractional-spacing mechanism is one of the essential features of thepresent invention, and I will now describe, it as it really forms a partof the space-selecting mechanism, though its operation does not begin.until after the insertion of the first permanent space by mechanism tobe hereinafter described.

As heretofore stated, between. the lower edge of the plate j and theupper edge of the stepped bar are a series of plungers K, formingdistance-pieces. There are as many sets of these plungers as there aredifferei'it numbers of spaces in the lines which the main the presentinstance. The number of plungers in the different sets varies from twoto twelve. These plungers appear best in Figs. 1, l, 6, 10, and. 12 to17,inclusive. The are contained in a suitable frame 7r, eonsisting of apair of side plates it" and Ir and end plates 7c" and I0 and partitions7r", dividing the frame into eleven vertical spaces. The plungers ineach instance fill the total width of the space and are frictionallyheld in the frame by suitable means, as the springs bearing againstthem.

In the sides of the side plates k and li are grooves 768, by which thefrai'ne is slidahly held to stationary gihs 7r, secured to thefran'le-bracket A The side plate lif of the frame has an extending arm7r, which is eonnected to a block It), Figs. 1, 2, l, and h. slidablymounted on a statioi'iary stud l. and. having at its lower end a pinlit, engaging in the collar g on the shaft g. Thus si multaneously withthe placement of the gears G the frame 7i? is given. a position eorrespending thereto. If the smallest gear t is in engagement with the rackll, as shown in Fig. l, the rearmost set of plungers K are directlybetween the plate j and the bar j". If the second gear engaged the rackii, the second set of plungers would occupy this position, and if thelargest gear engaged the rack the foremost set of plungers would hebetween. the plate 7"" and the bar j.

While the high face of the crown-earn is passing the roller g,(shortlyafter the eommencement of the rotation of the line-shaft i and hencewhile the gears and plungers are standing in their forward position, aplat form 7c, Figs. 1 and 4-, directly beneath the plungers is elevatedby means of the eam If engaging and raising the roller le on a link7.1-, which connects with such. platform. Thus upward movement of theplatform raises all the plungers into their initial posi tion againstthe lower face of the braeket It and the alined wall of the opening inthe frame-plate A as shown in Figs. 1' and t. In this position theplungers are held by friction produced by their springs It, whereforethe plunger-frame may be moved rearward, as stated, to select a set ofplungers corresponding to the number of spaces in the line.

The plungers K are peculiarly formed. in each set there are as manyplungers as there are spaces in the corresponding line. The lower endsof the plungers in any set are all of equal width, the individual widthvarviiig with the number of plungers in the set, and the aggregate widthbeing equal to a step of the bar j, while the upper ends with the exeeption of the last plunger in each set are all the same widthirrespective of their number or set, and the last plui'iger may he ofthe same width, but is preferably of a width chine is adapted to justifythat is, eleven sufficient to fill up the remaining spaee in I a- I IIIdistance across the frame, while at their upper ends one of the plungersis one-twelfth of the distance and the other plunger is eleven-twelfths.So for the ten-space set (shown in Fig. 16) the lower faces of each ofthe plungers are onetenth of the total distance, while the upper facesof nine of the plungers are one-twelfth of the distance, and the lastplunger is three-twelfths, though the width of its upper face istheoretically imm aterial, wherefore the characteristic of the plungersmay be stated to be that on one end of themin this case the lowerendtheir individual width is the total width. of the set divided by thenumber of spaces in the corresponding line. The upper ends of all exceptthe last in any set are the total width of the set divided by thegreatest number of spaces with which the machine is adapted to operate,and the width of the upper end of the last plunger in any set may be anyamount, but is preferably for convenience of construction the differencebetween the aggregate of all the preceding upper ends and the aggregatewidth of the lower ends, and, finally, the aggregate width of the lowerends is equal to a step of the bar with which these ends cooperate. Thischaracteristic of the plungers can be stated in formulae as follows: LetL equal width of lower ends of plungers, U equal width of upper ends ofplungers, (except the last one.) U equal width of upper ends of lastplunger, T equal total number of spaces which the machine may insert, Nequal number of spaces corresponding to any given set of plungers, Jequal length of a step of the bar j, (dependent upon the taper of thewedge and the ratio in gearing from the wedge to the bar.)

7 J J i lhen Lequals U equals U equals Now the plungers are allowedvertical movement independent of each other to an amount equal to therise of a step on the bar j. This movement is provided by gaps 7cbetween the overhanging edges of the plungers, except in the case of theset for the maximum number of spaces, Fig. 17, which have the same sizeabove as below and have no overhanging portions and are independentlymovable.

Connected with the plate j, Figs. 6 and 10, is a bar 7e havingon itsunder side teeth 7c, (twelve in number) which may be engaged by a pawl7r, operated by a bell-crank lever 76, which is connected by a link 10with another bell-crank lever k, which is connected to a link is, yokedaround the word-shaft N and operated by a cam 7c, which engages a roller7c on said link is and forces it to the right, Fig. 6, once for eachspace substituted. (This word-shaft N, as hereafter explained, rotatesonce for each space in the line, causing the substitution of a selectedpermanent space for the temporary spaces contained in the line.) Suchmovement of the link It operates to move the pawl 7r to the right, andthis pawl rising from beneath the bracket la h-by reason of the spring76, engages a tooth 16 and moves the bar 7: one tooth to the rightagainst the force of the spring j. The friction between the plate j andthe plungers holds the plate in the position it thus assumes. Thusimmediately following the insertion of each permanent space into theline the plate j is moved to the right a distance of one tooth 76 andthis distance is equal to the width of the upper end of each of theplungers K, except the last plunger, in the different sets. Now in theinitial position of the space-case the plate j is, as shown in Fig. 10,over all of the plungers of that set which is beneath it. As each spaceis replaced by a permanent space this plate j is moved to the right,Fig. 10, the distance of the width of top end of one plunger. Thismovement has no effect on the space-case as long as the plate j standson a plunger whose lower end is supported by the bar j; but as soon asthe plate 7' comes onto a plunger whose lower end is not thussupportedfor example, the third plunger shown in Fig. 10*the spring Fig.6, pulling downward through the arm 1' on the bar j will force that bar,the plate 7', and the remaining plungers downward until all theremaining plungers engage the next lower step on the bar j. This willbring downward the plate J one step, releasing the block 7' and allowingthe space-case to shift, under the influence of the spring 7' to bringthe next smaller size of permanent space into the ejection position.This size of space is therefore inserted for the remainder of the line,as the and slot, engaging, elevates the plate 7' to its uppermostposition by means of the arm and bar 7.

The taper of the measuring-wedge and the ratio of the theoretic gear fora one-space line are such as to cause movement of the stepped bar 9'through the length of one step for each one-hundredth of an inchthat is,the unit of difierence in size of the spaces of shortness in the line asmeasured. The series of permanent spaces are: first size, .03 inchthick; second size, .04: inch thick; third size, .05 inch thick fourthsize, .06 inch thick; fifth size, .07 inch thick sixth size, .08 inchthick; seventh size, .09 inch thick; eighth size, .10 inch thick; ninthsize, .1]. inch thick. The temporary space is .03 inch thick. When thesecond gear is engaged, this movement of the bar (by reason of thisreduced ratio between the gear 9 and the selected driving-gear G) isone-half of the length of a step of the bar for each one-hundredth inchof shortness in the length of the line, and likewise for each succeedinggear the movement of the stepped bar is equal to the length of its stepdivided by the theoretic number of the gear engaged. In other words, asstated, the portion of a step which is moved for each unit of shortnessof the line is the reciprocal of the number of spaces in that line.

Assuming that a line has six spaces in it, the sixth theoretic (fifthactual) gear will therefore be engaged, andv for each hun dredth of aninch of shortness in the line the stepped. bar will be moved one-sixthof the length of a step. Thus if such a line with temporary spaces inplace were still twelvehundredths of an inch short the movement ofthemeasuring-wedge would move the stepped bar twelve-sixths of thelength of a step, which would be two complete steps, bringing the set ofplungers entirely on the third step, (the zero position of the plungersbeing directly over the first step adjacent to the corner of the secondstep,) causing the insertion of spaces of the third size, eachfive-hundredths of an inch in thickness, which spaces thus aggregatethirty-hundredths of an inch. The temporary spaces withdrawn being ofthree-hundredths of an inch thickness, aggregate eighteen-himdredths,and thus the line has been expanded by the substitution the differenceof twelve-lunnlredths, which was the measured shortage. ever, that theline was eight-hundredths of an inch short. This, with six spaces in theline, would cause the bar to be moved eightsixths of the length of astep, or one and twosixths steps, thus causing the plungers to descendupon the third step two-sixths of its length from the end adjacent tothe second. step. The first space inserted, therefore, will be of thethird size or five-hundredths of an inch thick. After its insertion thefrac After its insertion Suppose, how-.

the plate j is again moved the width of a plunger, and thus comesentirely into the four remaining unsupported plungers, whereupon thespring 1', Fig. 6, brings down the stepped plate J, the bar j, plate 1,and the four remaining plungers the height of one step. This releasesthe block j and shifts the space-case to the next smaller size ofspaces. The third space will therefore be four-hundredths of an inchthick. Aft er the insertion of this space the plate j is again retractedthe width of one plunger top, as before; but all the remaining plunger-sare now supported on the second step, so that t his retraction is idle.The fourth, the fifth, and the sixth spaces are thus all of the secondsize. or four-lmndredths of an inch thick. The permanent spaces thusinserted are two of five-humlredths of an inch and four of fourhundredths of an inch, and the temper-arr sp aces'removed are six oftlnee-hul'nlredl hs of an inch, causing a net lengthening of the line of2 X .05+ :t .046 .03-that is, .l6=.18, or .08, which was the measuredshortage. It will thus appear that not more than two sizes of spaceswill ever be inserted in a single line, the aggregate width of the lowerends of any set of plungers never exceeding the length of a step on thebar f". When it happens that the entire set of plungers rest upon a stepwith the first plunger directly adjacent to the end of the next higherstep the spaces inserted in that line will all be of the same size, allthe subse iient movement of the plate j being idle.

Linc-advancing mcchaaism.'llhe line-advancing mechanism acts immediatelyalt er the lowering of the measuring-wedge to advance the line in aposition where its lirst temporary space can be replaced by a permanentspace. The mechanism thus aets before the fractional spacing mechanismwhich has been just described.

Slidable on a rail A, Figs. 5 and 5), parallel with thejustifyingchannel, is afollowerblock B. Leading from the left-hand end,Fig. 1, of this block and descending over a pulley is a cord 7), havingattached at its lower end a weight I)", wherefore the block is giventendency to return to its initial position. Depending from. the block isan arm 6 extending into the type-channel and engaging a follower if toshove along the type. A dog I), pivoted. in this bloc and pressed by aspring against the rail A, tends to re tain the block in whateverposition it ma v be after it has been. advanced. For ad \ant-ing theblock I provide a cord b which passes rearward and then downward from apulley and finally around a drum b", which drum is on a shaft 1),pivoted in a suitable floating framework I). On the other end of thisshaft is a gear 6 adapted to be brought int n mesh with a gear 6 looselyournaled on the shaft N and constantly rotated.

lOO

Following the lowering of the measuringwed e a cam ro'ection on the hubof one which the link connects, and withdrawing a lug b on that arm froma projection on the frame I). The frame thus drops slightly downwardunder the influence of the spring until its projection comes in front ofthe lug Z1 whereupon the return of the arm I) under the influence of thespring I) swings the frame 5 forward, bringing the gear into mesh withthe gear I). This rotates the drum 1), drawing down the cord andadvancing the block B,and with it the follower b and line of type Z. Astype are advanced they press downward the beveled face of the lever P,Figs.6, 19, and 20, and this presses latter springs up into the notch ofthe temporary space, and the succeeding type engages the front face ofthe nose and shoves the lever P rearward the slight distance which theslot p in the lever allows. This stops the advancing line and alsoswings the lever 21 and initiates the rotation of the word-shaft, whichcauses the substitution of permanent spaces for the temporary spaces.This will be described hereinafter. When the line is brought to a stop,as described, the continued rotation of the line-advancing shaft 1)causes the drum 6 to wind up on the now-locked cord b thus raising thefloating frame Z2 until its projection clears the lug b whereupon thisframe is moved backward by the spring I), disengaging the gears I1 andb? and stopping the rotation of the drum.

ll have now completed the enumeration of the operations initiated by theline-shaft, and they may be summarized as follows: First, the cam jshifts the space-case to the extreme left and raises the stepped blockJ. Second, the crown-cam gnioves the gears and plungers forward,withdrawing the gears from engagement with the rack H and permittingthem to be rotated back to their zero position by the spring 9 actingthrough the shaft 9. Third, the cam moves the space-accounting plate 0to the right and back, again locating the rack H, and simultaneously thecam 1c raises the platform 7r beneath the plungers. Fourth, the campiece8 on the side of the camf releases the qaace-accounting pawls. Fifth,the crowncam 9 allows the return of the gears and plungers until theyare stopped by a gear engaging the rack. Sixth, the cam f allows thewedge to rise, rotating the gears and shifting the bar j Seventh, thecam j lowers the stepped block J and primarily locates the space-case.Eighth, the cam j lowers the wedge to initial position. .l inth, the camprojection b throws into action the line-advancing mechanism.

S pace-substituting mechanism .-As stated, the final operation of theline-shaft is to initiate the operations of line-advancing mech-' anism,which draws the line forward until stopped with its first temporaryspace over the nose of the triplever P, with that .lever shoved rearwardas far as the short slot p allows. This slight movement swings thepivoted lever 12 Fig. 6, which bears at its lower end against an arm pon a rock-shaft p secured. to the other end of which is an arm 2), Fig.9, depending from which is a link 29 This link is suitably guided at itslower end and normally operates to hold in idle position the pawl 19* ona disk 1)". The rocking of the lever 12, however, raises the link 1')and releases this pawl, whereupon it springs into engagement with acontinuously rotating clutch member p loose on the word-shaft N. Thedisk p is rigid on the word-shaft, and thus rotation of the latter isinitiated. The first movement of the shaft N is to bring a decreasingface of the cam 9, Figs. 1 and 3, into engagement with the roller 9 onthe link (1 and this, acting through the arm and rock-shaft q, allowsthe ejectorarm g to be drawn forward by the spring 1 Fig. 4. The upperend of this ejector-arm is connected by a link (1 with the ejector-barQ. The space-case I is located directly in front of the ejectonbar, andthe latter, being advanced by the spring q, shoves out of the space-casethe lower space from that channel of the space-case which thespaceselecting mechanism heretofore described holds in front of theejector.

The space is ejected into a barrel L, Figs. 5 and 7, which I call thespace-turner and which carries peripheral teeth meshing with a rack Z.This rack is connected by a bellcrank Z with a link Z whose lower endyokes around the shaft N. Just after the space has been injected intothespace-turner and while a concentric face of the cam g is rotatingpast the roller q a decreased face on a cam Z acting on a roller Z ofthe link Z allows the spring Z to swing the bell-crank lever Z to turnthe space-turner ninety degrees, thus turning the space from its flatside to a position on edge. This same movement of the rack Z releasesthe arm Z Figs. 5, 19, 20, whose spring Z moves it to the left,whereupon it engages an arm Z carried by the lever P and having a nosewhich stands within the notch of the temporary space, and swings thisarm to shove forward that portion of the line which is in-advance of thetemporary space engaged. This opens a gap l in the line for theinsertionof the permanent

